Impulse pump

ABSTRACT

An impulse pump is provided with a low power motor to store rotational kinetic energy in a flywheel. The stored kinetic energy is released using a planetary gear transmission that links the flywheel to a pusher shaft. The kinetic energy is released when the planetary gear carrier is decelerated using a caliper brake. The planetary gear carrier deceleration forces rotational acceleration of the pusher shaft and deceleration of the flywheel. Through a cam roller contact point between the pusher shaft and the cam raceway on the plunger; the rotational motion of the pusher shaft is converted to linear and translational motion of the plunger. The translational motion of the plunger allows impulse jet energy to be rapidly released from a nozzle of the pump.

STATEMENT OF GOVERNMENT INTEREST

The invention described herein may be manufactured and used by or forthe Government of the United States of America for governmental purposeswithout the payment of any royalties thereon or therefor.

CROSS REFERENCE TO OTHER PATENT APPLICATIONS

None.

BACKGROUND OF THE INVENTION (1) Field of the Invention

The present invention relates to an impulse pump for generating a pulsedfluid jet.

(2) Description of the Prior Art

High velocity water jets are used in water jet cutting systems. Methodsand systems exist to generate high pressures (often over 345MegaPascals) needed for the high velocity water jets. A known system isto use a reciprocating piston pump to produce fluid flow at a fixed flowrate and pressure.

In operation, the output of the reciprocating pump is sent to areservoir or attenuator capable of handling high pressure and is thendischarged through a valve or orifice. This type of system is designedto provide a steady jet of high velocity water. However, the system isnot adaptable for providing short duration pulses of water.

High-velocity (exceeding 300 meters per second) short-duration (lessthan 1 second) water jets can be used in underwater demolition byutilizing the effects of water-hammer and cavitation bubble collapse.Technical challenges related to generating the high-velocityshort-duration water jets include: storage of mechanical energy; a rapidrelease of the stored energy; and conversion of the released energy toform a water jet. For example, in U.S. Pat. No. 7,926,587, entitled“Explosive Water Jet with Precursor Bubble”, a method is described forcreating a pulsed water jet by using explosively released chemicalenergy.

Other systems exist to convert stored mechanical energy to an impulsestarted motion (an impact). In these systems, a mechanical spring isslowly compressed and then quickly and fully released to provide asudden burst of energy to drive the impulse motion.

Other methods to store energy can be used to drive an impulse or impactdevice. Pneumatic and hydraulic systems can store energy that isreleased through a rapidly activated valve. Also, electrical energy canbe converted to mechanical motion through electromagnetic forces such aselectrical solenoids.

Desired characteristics of an improved energy storage and releasesystems are that the apparatus, device, or system has: a higher energystored per unit mass of the overall system; a higher efficiency ofenergy conversion during energy release; and a rapid rate of energyrelease.

SUMMARY OF THE INVENTION

It is therefore an object of the present invention to provide an impulsepump that can quickly release water jet energy.

To attain the object described, the present invention assemblescomponents suitable for: storage of energy in the form of rotationalkinetic energy; a rapid release of the stored energy; conversion of thereleased rotational energy into linear motion; and a use of the linearmotion to pressurize fluid with impulse energy.

The present invention uses a low power motor to store rotational kineticenergy in a flywheel. The stored energy is released using a planetarygear transmission that links the flywheel to a pusher shaft. The energyrelease is achieved when the planetary gear carrier is decelerated usinga caliper brake. The planetary gear carrier deceleration forcesrotational acceleration of the pusher shaft and deceleration of theflywheel. Through a cam roller contact point between the pusher shaftand the cam raceway on the plunger; the rotational motion of the pushershaft is converted to a linear and translational motion of a plungerdevice. The translational motion of the plunger rapidly empties areservoir of the pump and creates a highly pressurized fluid pathexiting a nozzle of the pump.

The pressurized fluid can drive a high-velocity short-duration waterjet, with the qualities of a high energy storage-to-system weight ratio,efficient energy conversion, and a rapid energy release. Additionally,the present invention combines components known in the art, including anelectric motor, a flywheel, a planetary gear clutch, hydraulic caliperbrakes, a barrel type cam and follower, a piston pump, a reservoir, anda nozzle to assemble the inventive pump.

BRIEF DESCRIPTION OF THE DRAWINGS

A more complete understanding of the invention and many of the attendantadvantages thereto will be readily appreciated as the same becomesbetter understood by reference to the following detailed descriptionwhen considered in conjunction with the accompanying drawings wherein:

FIG. 1 depicts an impulse pump built according to the teachings of thepresent invention with a portion of the housing removed to show internalcomponents of the pump;

FIG. 2 depicts a cross-section of the impulse pump of the presentinvention;

FIG. 3 depicts an enlarged view taken from FIG. 2 as sectioned area 3-3;

FIG. 4 depicts an enlarged view taken from FIG. 2 as sectioned area 4-4;

FIG. 5 depicts an enlarged view taken from as sectioned area 5-5;

FIG. 6 depicts a partial cross-section of the impulse pump with thecross-section showing as associated drive gear engaged with a flywheelrim gear with the view taken from reference lines 6-6 of FIG. 2;

FIG. 7 depicts a partial cross-section of the impulse pump with thecross section showing an associated ring gear, planetary gears,planetary gear carrier, sun gear, and pusher shaft with the view takenfrom reference lines 7-7 of FIG. 2;

FIG. 8 depicts a cross-section of the plunger placement in the headblock of the impulse pump of the present invention;

FIG. 9 depicts an isometric view of a pusher shaft of the presentinvention with the view also showing the shape of an associated camrace-way;

FIG. 10 depicts an isometric view of a plunger of the present inventionwith the view showing the integral cam roller and spring of the pump;

FIG. 11A-11D depict the plunger, spring, head block, nozzle, and pushershaft of the present invention in four phases of an actuation cycle ofthe pump; and

FIG. 12A-12D show the rotational speed of the flywheel and therotational angle of the pusher shaft along with sequencing of aplanetary gear carrier brake caliper and an idler disk brake caliperreferenced to the four phases of an actuation cycle of the pump.

DETAILED DESCRIPTION OF THE INVENTION

Water jet pulses are useful in cutting and demolition applications. Theinstantaneous pump power requirements to create water jet pulses arehigh relative to a system imparting an equivalent average energy to awater stream at a uniform flow rate. To create a high energy water jetpulse; energy can be transferred into the system using a relatively lowpower drive which is stored in a rotation of a flywheel. Energy can berapidly released by converting the rotational motion of the flywheelinto a linear motion of a piston or plunger.

A preferred embodiment of an inventive impulse pump 15 is shown inFIG. 1. In the figure, the pump 15 generally comprises a drive motor 17,a planetary gear and flywheel gear box housing 20, a cam assemblyhousing 70 attached to the gear box housing 20, a plunger 72, a headblock 90, and a nozzle 92. Details of the gear box housing 20, the camassembly housing 70 and the head block 90 are depicted in FIG. 2 throughFIG. 10.

In operation, linear motion of the plunger 72 forces fluid through thenozzle 92 to form an impulse jet 100 into a liquid environment 200 orother suitable environment. The impulse jet formation is achieved byalternately drawing fluid into a reservoir 94 through the nozzle 92 fromthe liquid environment 200 and subsequently forcing the fluid from thereservoir through the nozzle into the liquid environment 200.

The fluid is drawn into the reservoir 94 when rotating a pusher shaft 22in a first angular direction to a second angular position in a rotationdirection. An impulse pulse of fluid thru the nozzle 92 is created whenthe pusher shaft 22 is rotated in from the second angular position tothe first angular position in the same rotational direction; thereby,completing a full rotation. Rotating the pusher shaft 22 results in themovement of a cam race-way 74. This movement changes the axial locationof a contact point between a cam roller 76 and the cam race-way 74relative to the nozzle 92. Contact between the plunger 72 and the camrace-way 74 is maintained by a spring 78.

An impulse jet 100 is formed by forcing liquid out of the reservoir 94through the nozzle 92 by downward motion of the plunger 72. The downwardmotion is forced by rotation of the pusher shaft 22 with the associatedmovement of the cam race-way 74. Rotation of the pusher shaft 22 causesa cam follower arm 80 to be forced downward through the cam roller 76 asthe contact roller follows the cam race-way 74. A sleeve bearing 98 isplaced between the plunger 72 and the head block 90 to minimize frictionand to prevent flow of fluid from the reservoir 94 into the cam assemblyhousing 70 when drawing water into or expelling water from thereservoir.

In a further description of the arrangement of the impulse pump 15; thedrive motor 17 is mounted to a base plate 24. The drive motor 17 drivesa flywheel rim gear 26 through a drive shaft 28 and a drive gear 30 (SeeFIG. 3). Roller bearings 32 or their equivalent are positioned at movingareas throughout the pump 15 in order to reduce friction in those areas.The bearings are not all identified in the figure but have generally thesame shape and function as the identified bearing 32.

In FIG. 3, the drive gear 30 engages with the flywheel drive gear 26which is attached to a flywheel 34. The drive gear 30 can be driven atpredetermined rotational speeds required to store the desired energy inthe flywheel 34. The rotational speed may be near zero if the requiredenergy is small or very high (up to the structural and vibrationallimits of the system, e.g., multiple thousands of revolutions perminute) if the required energy is large.

In operation and prior to actuation of the impulse pump 15, the pushershaft 22 is held in a fully retracted position. The pusher shaft 22 isheld in a fixed position by an idler disk caliper 48 (See FIG. 4). Whenthe idler disk brake caliper 48 is activated through movement of ahydraulic piston 50; frictional pads 52 are clamped against the surfaceof an idler rotor 54 and the idler rotor is held in place.

While the idler rotor 54 is held in place, a planetary gear carrier 42must be allowed to rotate by depressurizing a hydraulic cylinder 56. Ifboth the idler rotor 54 and the pusher shaft 22 are simultaneously heldin place, all internal components of the pump 15 will be forced to stop.As shown in FIG. 5, a planetary gear carrier brake caliper 46 isreleased by depressurizing the hydraulic cylinder 56. Thedepressurization of the hydraulic cylinder 56 eliminates the contactforces between friction pads 60 and the planetary gear carrier 42 sothat the planetary gear carrier is free to rotate.

FIG. 7 depicts the flywheel 34 attached to a ring gear 36. The ring gear36 is a component in the gear box housing 20. The ring gear 36 mesheswith planetary gears 38 and the planetary gears mesh with a sun gear 40.The sun gear 40 is attached to the pusher shaft 22. The planetary gears38 are attached to the planetary gear carrier 42 (not shown in FIG. 7)by planetary gear shafts 44.

Referring again to FIG. 2, while the plunger 72 is fully retracted andthe pusher shaft 22 is held stationary; the drive motor 17 canaccelerate the flywheel 34 to a desired speed. In this way, energy isstored in the flywheel 34 in the form of rotational kinetic energy.Through kinematics of the planetary gear 38, the planetary gear carrier42 rotates at a fraction of the rotational speed of the flywheel 34.

To convert the rotational energy of the flywheel 34 to a linear motionof the hydraulic piston 50; the idler rotor 54 is released bydepressurizing the idler brake caliper 48. The planetary gear carrier 42is subsequently decelerated by actuating the brake caliper 46. Theplanetary gear carrier brake caliper 46 is mounted to a positioningplate 58.

The planetary gear carrier brake caliper 46 is activated throughexpansion of the hydraulic cylinder clamping frictional pads 60 againstthe surface of the planetary gear carrier 42 (See FIG. 5). In responseto the clamping applied to the planetary gear carrier 42; the flywheel34 experiences a decelerating torque while the pusher shaft 22experiences an accelerating torque.

As shown in FIG. 8, the plunger 72 has a square cross-section and isonly free to move along a central pump axis 62 of the impulse pump 15.The sleeve bearings 98 are affixed to the head block 90 to ease axialmotion while the plunger 72 is under torsional loads.

The pusher shaft 22, shown in detail in FIG. 9, includes the contouredcam race-way 74. The cam race-way 74 is a surface machined onto an endof a large diameter portion of the pusher shaft 22 to form a barrel cam.Barrel cams are well known in the art as a means to convert rotationalmotion to linear motion. The cam function is realized when the pushershaft 22 rotates and the elevation of the race-way contact pointchanges.

The elevation of the race-way contact point is defined as the distancealong a line parallel to the pump axis 62 measured from a fixed point ona plane perpendicular to an axis of the pusher shaft 22 to the point atwhich the cam race-way 74 contacts the contacts the cam roller 76. Overthe course of one half revolution of the pusher shaft 22; the elevationof the race-way contact point varies from a maximum distance from thenozzle 92 to a minimum distance.

The plunger 72, shown in detail in FIG. 10, is attached to the camroller 76 that contacts the cam race-way 74 at a fixed rotationallocation. The plunger 72 does not rotate relative to the head block 90.As the pusher shaft 22 rotates and the elevation of the race-waycontacts point varies from a maximum distance from the nozzle 92 to aminimum distance; the plunger 72 is forced downward and axially throughcontact of the cam roller 76 with the cam race-way 74 and a jet of fluid100 is formed at the nozzle,

As the pusher shaft 22 rotates and the elevation of the race-way contactpoint varies from a minimum distance from the nozzle 92 to a maximumdistance; the spring 78 forces upward motion of the plunger 72. Theupward force maintains contact between the cam roller 76 and the camrace-way 74. The upward motion of the plunger 72 draws fluid into thereservoir 94 thru the nozzle 92. Thrust bearings 82 allow the pushershaft 22 to rotate under axial loads (See FIG. 11 for rotation of thepusher shaft).

Returning to FIG. 2, an angular position monitoring sensor 64 isincluded to assist in an actuation sequencing of the planetary gearcarrier brake caliper 46 and the idler disk brake caliper 48. Themonitoring sensor 64 detects angularly positioned markings placed on thecircumference of the idler rotor 54 to establish a rotational positionof the rotor.

FIG. 11A, FIG. 11B, FIG. 11C, and FIG. 11D depict four positions of thepusher shaft 22 and the plunger 72 during a rotation of the pushershaft. In position 11A, the flywheel 34 is at full rotational speed (asindicated by direction arrow “A”); the plunger 72 is fully retracted;the reservoir 94 is full of liquid; and the plunger is held in positionby the idler brake caliper 48 (the flywheel and idler brake caliper arenot shown in this figure). The impulse jet 100 is initiated by releasingthe idler brake caliper 48 and actuating the planetary gear carrierbrake caliper 46 (the brake caliper is not shown in this figure).Through transfer of forces from the planetary gear carrier brake caliper46 to the flywheel 34; the flywheel is decelerated and the pusher shaft22 is rotated (as indicated by direction arrow “A”).

In position 113, the plunger 72 is forced downward through the camroller 76 as the contact point with the cam race-way 74 moves downward.Liquid is forced from the reservoir 94 as the plunger 72 moves downward.

In position 11C, the plunger 72 is at its lowest position. The planetarygear carrier brake caliper 46 is released and the idler brake caliper 48is engaged to stop rotation of the pusher shaft 22. The angular positionmonitoring sensor 64 monitors rotation of the pusher shaft 22 to timeactuation and release of the calipers 46 and 48.

Movement from position 11C to position 11D is achieved by releasing theidler disk brake caliper 48. Fluid is drawn into the reservoir 94 byreleasing the idler disk brake caliper 48 and partially engaging theplanetary gear carrier brake caliper 46. Engaging the planetary gearcarrier brake caliper 46 causes the pusher shaft 22 to rotate. Duringthe rotation, the contact points between the cam roller 76 and the camrace-way 74 translates upward parallel to the pump axis 62 while drawingfluid into the reservoir 94 through the nozzle 92. Contact between thecam roller 76 and the cam race-way 74 is maintained through action ofthe spring 78. The spring 78 provides the force necessary to move theplunger 72.

The planetary gear carrier brake caliper 46 is released and the idlerbrake caliper 48 is engaged as the plunger 72 returns to a top position.The angular sensor 64 is monitored so that the motion of the plunger 72is stopped at the correct position. The pulse jet sequence can then berepeated once the flywheel 34 has returned to a full pre-pulserotational speed.

FIGS. 12A-12D show the rotational speed of the flywheel and therotational angle of the pusher shaft 22 along with the sequencing theplanetary gear carrier brake caliper 46 and the idler disk caliper brake48 referenced to the four phases of the actuation cycle of the pump 15.

The primary advantages of the impulse pump 15 are twofold. First, theimpulse pump 15 enables the rapid conversion of rotational kineticenergy stored in a flywheel 34 to a linear motion of the plunger 72 toform the short duration impulse jet 100. The process of collectingenergy from the low power drive motor 17 over a long period relative tothe duration of the impulse jet 100 and rapidly converting that energyallows the overall size of the pump 15 to be small as compared to adevice engineered with a drive motor capable of producing theinstantaneous power requirements of the water jet production.

Second, the caliper brakes 46, 48 are sequenced to apply forces tocomponents within the planetary gear system to rapidly decelerate andaccelerate components within the impulse pump 15 in order to produce arapid and forceful motion of the plunger 72. The rapid motion of theplunger 72 creates the water (impulse) jet 100. The rapid motion of theplunger 72 may be used for other applications other than the formationof a water jet. The impulse pump 15 with rapid motion of the plunger 72may be used in punch presses or similar devices where short durationforceful motion of a linear actuator is needed.

What has thus been described is a device for creating a short durationand high velocity water jet 100. The short duration and high velocitywater jet 100 is created by the impulse pump 15 of the present inventionby storing energy in a flywheel 34 that is rapidly converted to linearmotion of a piston or plunger 72. The linear motion of the plunger 72forces water through a nozzle 92 to form the water jet 100.

Central to the energy conversion process are the two caliper brakes 46,48 that provide deceleration and restraining forces to components of theimpulse pump 15. The pusher shaft 22 is held in place as the flywheel 34is accelerated. When the flywheel 34 is at full speed, the idler diskcaliper brake 48 is released and the planetary gear carrier brakecaliper 46 is applied. A counter-torque is transferred to the pushershaft 22 in reaction to the torque applied to the planetary gear carrier42 by the planetary gear carrier brake caliper 46.

This counter torque rotates the pusher shaft 22, which in turn forcesthe plunger 72 downward and expels pressurized fluid 100 from thereservoir 94 thru the nozzle 92. Work done on the system throughapplication of the planetary gear carrier brake caliper 46 isproportional to the frictional force applied by the planetary gearcarrier brake caliper times the speed of the pump components on whichthe disk brake acts.

The energy to perform that work is provided by the flywheel 34 anddeceleration of the flywheel. Energy from the flywheel 34 is lostthrough the generation of heat during application of the system brakeand transferred to other system components through a rotationalacceleration of the pusher shaft 22, linear acceleration of the plunger72, and work done on the fluid that forms the pressurized fluid jet 100.

The drive motor 17 for the impulse pump 15 can be comparatively smallbecause the instantaneous power requirements of the drive system arelow. Because acceleration of the flywheel 34 can be slow; the drivemotor 17 need only have power slightly in excess of that required toovercome system losses at a maximum flywheel rotational speed.

Many modifications and variations of the present invention may becomeapparent in light of the above teachings. A number of alternativedevices could be constructed using the same general methods discussedherein to construct devices that would be optimized for a particularpurpose. For example: the bearing types and configurations may bedifferent than as shown; disk brake calipers could be replaced withdrum, inductive, hydraulic, or band brakes; and the barrel cam andfollower design could be replaced with a swashplate assembly.

In light of the above, it is therefore understood that within the scopeof the appended claims, the invention may be practiced otherwise than asspecifically described.

What is claimed is:
 1. A pump for generating impulse energy in the formof a water jet, said pump comprising: a base plate positionedperpendicular to a longitudinal axis of said pump, said base plateincluding an inner surface, an outer surface, a central aperturecollinear to the longitudinal axis and at least one aperture at a radialdistance from the central aperture; a first bearing positioned withinthe central aperture; a pusher shaft collinear with the longitudinalaxis, said pusher shaft having a plurality of axial sections ofascending diameter adjacent to each other and extending away from theinner surface of said base plate, a smallest diameter section centeredwithin and engaging said first bearing, a second section of increaseddiameter compared to said first section, a third section of increaseddiameter compared to said second section, a fourth section of increaseddiameter compared to said third section, a fifth section of increaseddiameter compared to said fourth section, a sixth section of increaseddiameter compared to said fifth section and a seventh section ofincreased diameter compared to said sixth section; an idler rotorpress-fit to encompass said second section with a plane of said rotorperpendicular to the longitudinal axis, said idler rotor havinguniformly spaced markings around a circumference; a sensor attached tothe inner surface of said base plate and in proximity to said idlerrotor, said sensor capable of detecting and reading the uniformly spacedmarkings of said idler rotor; a first brake caliper including ahydraulic cylinder, said first brake caliper attached to said base plateand bracketing said idler rotor such that when said first brake caliperis actuated, a restraining force is applied by said hydraulic cylinderto said idler rotor and onto said pusher shaft; a second bearingencompassing said third section; a flywheel radially affixed to saidsecond bearing; a positioning plate positioned at an axial locationcoincident with said sixth section such that rotational motion iscapable between said pusher shaft and said positioning plate; a thirdbearing positioned within the radially distanced aperture of said baseplate; a drive motor having an attached drive shaft with said motorspaced apart from the outer surface of said base plate and with saiddrive shaft rotationally positioned within and extending through saidthird bearing; a motor drive gear attached coaxially to an end of saiddrive shaft opposite to the attachment of said drive shaft to saidmotor, wherein said drive gear is capable of rotating at a predeterminedspeed; a flywheel rim gear parallel to and mechanically affixed to saidflywheel on a face of said flywheel facing said base plate wherein arotational speed is capable of being transmitted from said motor drivegear and said flywheel rim gear onto said flywheel; a ring gearmechanically attached to said flywheel and positioned collinear with thelongitudinal axis at a position coincident with said fourth axialsection, said ring gear annularly shaped with teeth on an inner rim; asun gear positioned collinear with the longitudinal axis and at a sameposition along the longitudinal axis as said ring gear, with teeth on anouter rim, and secured to said pusher shaft on said fourth axialsection; a plurality of planetary gears distributed circumferentially inan annular space between said sun gear and said ring gear at a sameposition along the longitudinal axis as said ring gear and said sungear, each of said planetary gears having a diameter equal to adifference in radii of said ring gear and said sun gear, with teeth onan outer rim to simultaneously mate with said ring gear and said sungear, and each of said planetary gears having a central aperture; afourth bearing surrounding said fifth axial section; a disk shapedplanetary gear carrier affixed to said fourth bearing, said planetarygear carrier having a central aperture, and multiple attachment pointsdistributed circumferentially at a radial offset equal to an averageradius of an outer diameter of said sun gear and an inner radius of saidring gear; a plurality of planetary gear shafts with each of saidplanetary gear shafts rigidly attached perpendicular to a surface ofsaid planetary gear carrier at each of said multiple attachment pointswith each of said planetary gear shafts supporting each of saidplanetary gears; a plurality of planetary gear bearings, each of saidplanetary gear bearings positioned in each of said central apertures ofsaid planetary gears to allow rotation of said planetary gears aboutsaid planetary gear shafts; a tubular gear box housing coaxial with thelongitudinal axis, said tubular gear box housing attached to said baseplate on one end and said positioning plate on another end and enclosingsaid flywheel, said idler rotor, said sensor, said first brake caliper,said motor drive gear, said flywheel rim gear, said ring gear, said sungear, said planetary gears, said planetary gear bearing, said planetarygear carrier and said planetary gear shafts; a second brake caliper withhydraulic cylinder within said tubular gear box housing, said secondbrake caliper attached to said positioning plate and bracketing saidplanetary gear carrier such that when said second brake caliper isactuated, said hydraulic cylinder is capable of applying a restrainingforce to said planetary gear carrier and when said second brake caliperis inactivated, said hydraulic cylinder removes the restraining forcethereby allowing said planetary gear carrier and said flywheel torotate; a thrust bearing positioned coaxially to the longitudinal axisat a position along the longitudinal axis coincident and secured to saidseventh section of said pusher shaft wherein said thrust bearing iscapable of allowing said pusher shaft to rotate under axial loads whiledampening longitudinal loads toward said positioning plate; a tubularcam assembly housing, said tubular cam assembly housing coaxial with thelongitudinal axis and attached at a first end to said positioning plateon a side of said positioning plate opposite to said tubular gear boxhousing; a cam assembly within said tubular cam assembly housing, withsaid cam assembly attached to said pusher shaft at an end opposite to anend of said pusher shaft at said first bearing with said cam assemblyhaving a contoured cam race-way on a second end; a cam follower armextending laterally from the longitudinal axis to an offset radiallocation, said cam follower arm having a cam roller in rotationalcontact with said cam race-way at the offset radial location; a plungerpositioned coaxially with the longitudinal axis, said plunger having asquare cross-section portion attached to said cam follower arm and acylindrical portion extending away from said square cross-sectionportion along the longitudinal axis; a head block positioned coaxiallywith the longitudinal axis and encompassing said head plunger, said headblock have a central bore divided into three sections; a shallowcircular bore at a flanged end of said head block, a square section of asmaller cross sectional area than said first circular bored sectionextending axially from an end of said first circular bored section to asecond axial location, and a second circular section extending from anend of said square section to an unflanged end of said head blockwherein said second circular section is a reservoir for said pump; aplurality of sleeve bearings positioned between a surface of said squaresection of said head block and said plunger; a compression springpositioned coaxially with the longitudinal axis between said shallowcircular bore at the flanged end of said head block and said camfollower arm wherein contact between said plunger and said cam followerarm is maintained by said compression spring; and a circular platepositioned at an unflanged end of said head block with an aperture at acenter of said circular plate to form a nozzle; wherein said drive motoris capable of accelerating the flywheel to a predetermined speed as saidpusher shaft is held stationary such that energy is stored in saidflywheel as rotational kinetic energy and the rotational kinetic energyis applied as an accelerating torque from said flywheel to said pushershaft when said flywheel decelerates; wherein rotating said pusher shaftin a first direction results in movement along the longitudinal axis forrolling said cam way wherein the fluid is drawn into said reservoir bymovement of said plunger to said base plate; wherein rotating saidpusher shaft in a second direction results in movement along thelongitudinal axis for rolling said cam way wherein the fluid forced fromsaid reservoir and said nozzle by movement of said plunger away fromsaid base plate.